EP0334994B1 - Flüssigkeitsfördernde Kolbenpumpe - Google Patents

Flüssigkeitsfördernde Kolbenpumpe Download PDF

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Publication number
EP0334994B1
EP0334994B1 EP88116666A EP88116666A EP0334994B1 EP 0334994 B1 EP0334994 B1 EP 0334994B1 EP 88116666 A EP88116666 A EP 88116666A EP 88116666 A EP88116666 A EP 88116666A EP 0334994 B1 EP0334994 B1 EP 0334994B1
Authority
EP
European Patent Office
Prior art keywords
delivery
plunger
pump
driving motor
speed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88116666A
Other languages
English (en)
French (fr)
Other versions
EP0334994A1 (de
Inventor
Shigeaki Fujimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shimadzu Corp
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Shimadzu Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shimadzu Corp filed Critical Shimadzu Corp
Publication of EP0334994A1 publication Critical patent/EP0334994A1/de
Application granted granted Critical
Publication of EP0334994B1 publication Critical patent/EP0334994B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N30/00—Investigating or analysing materials by separation into components using adsorption, absorption or similar phenomena or using ion-exchange, e.g. chromatography or field flow fractionation
    • G01N30/02—Column chromatography
    • G01N30/26—Conditioning of the fluid carrier; Flow patterns
    • G01N30/28—Control of physical parameters of the fluid carrier
    • G01N30/36—Control of physical parameters of the fluid carrier in high pressure liquid systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0209—Rotational speed
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N30/00—Investigating or analysing materials by separation into components using adsorption, absorption or similar phenomena or using ion-exchange, e.g. chromatography or field flow fractionation
    • G01N30/02—Column chromatography
    • G01N30/26—Conditioning of the fluid carrier; Flow patterns
    • G01N30/28—Control of physical parameters of the fluid carrier
    • G01N30/32—Control of physical parameters of the fluid carrier of pressure or speed
    • G01N2030/326—Control of physical parameters of the fluid carrier of pressure or speed pumps

Definitions

  • the invention relates to a reciprocating type fluid delivery pump with two pump heads, comprising: a driving motor; a pair of plungers for driving said two pump heads, respectively; a converting means for converting the rotational motion of said driving motor into reciprocating motion of each plunger, wherein said converting means includes a cam means, engageable with said plungers, for reciprocating said plungers, and wherein said cam means has such a configuration that, when the driving motor is rotated at constant velocity, the delivery flow rate during the delivery starting period of each of the plungers is in excess of that during the other periods of the cycle; and a means for selectively decelerating said driving motor during said excess delivery period when fluid delivery is not carried out under high pressure; wherein said cam means is designed such that the delivery speed of each plunger has a first rise while the delivery speed of the other plunger is still constant and a second rise while the delivery speed of the other plunger decreases.
  • the present invention relates to a so-called small-volume plunger reciprocating type fluid delivery pump which may be used, for example, to deliver a mobile phase in liquid chromatography.
  • a typical conventional small-volume plunger reciprocating type fluid delivery pump has a driving motor, plungers for driving two pump heads, respectively, and a converting mechanism for converting the rotational motion of the driving motor into a reciprocating motion of each plunger.
  • Fig. 4 shows the plunger speed characteristics with respect to an angle ⁇ of a conventional small-volume plunger reciprocating type fluid delivery pump having two pump heads.
  • the curve 1 shows the plunger speed characteristics of the first pump head, while the curve 2 shows the plunger speed characteristics of the second pump head.
  • a cam is used as a converting mechanism for converting the rotational motion of the driving motor into a reciprocating motion of each plunger.
  • the axis of ordinates i.e., dr/d ⁇ (r is the distance from the center of rotation of the cam), represents the plunger speed at the time when the driving motor is rotating at a constant velocity.
  • the upper and lower sides of the axis of abscissas show the plunger speeds at the deliver and suction sides, respectively.
  • the cam is shaped such that dr/d ⁇ shows a trapezoidal pattern.
  • the flow rate of the fluid being delivered which is the sum of the respective delivery flow rates of the two pump heads, is constant throughout all angles of the cam when the driving motor is rotated at constant velocity, as shown by the reference numeral 3 in Fig. 4.
  • US-A-Re. 31 608, Magnussen, Jr. discloses a fluid pump mechanism for delivering fluid against a back pressure which comprises a piston movable within a chamber for drawing fluid into the chamber during a chamber filling interval, pressurizing the fluid during a pressurizing interval wherein the fluid pressure attains an effective delivery value prior to delivery from the chamber and delivering the pressurized fluid from the chamber during a delivery interval of piston movement, and means for controlling the rate of piston movement such that the piston moves at a predetermined rate during delivery of the pressurized fluid.
  • the controlling means includes a "pump-up" means for establishing a greater rate of piston movement during the pressurizing of the fluid, for signalling completion of fluid pressurization, and for thereupon establishing the predetermined rate of piston movement for effecting delivery of the pressurized fluid from the chamber, thereby increasing the time during which fluid is delivered to a receiving system and decreasing the time of filling or refilling and pump-up prior to such delivery, and thus enabling fluid to be delivered at a given flow rate and with a greatly reduced pulsation.
  • a "pump-up" means for establishing a greater rate of piston movement during the pressurizing of the fluid, for signalling completion of fluid pressurization, and for thereupon establishing the predetermined rate of piston movement for effecting delivery of the pressurized fluid from the chamber, thereby increasing the time during which fluid is delivered to a receiving system and decreasing the time of filling or refilling and pump-up prior to such delivery, and thus enabling fluid to be delivered at a given flow rate and with a greatly reduced pul
  • US-A-4 045 343, Achener et al. discloses a high pressure liquid chromatography system including a reservoir for a liquid mobile phase, an LC column and detector, a high pressure reciprocating pump for enabling flow from the reservoir through the column, and a positively actuated inlet valve for controlling flow from the reservoir to the pump chamber.
  • the pump is driven by motor means, such as a stepping motor, directly coupled thereto; and the inlet valve is actuated by the power train of the motor and pump, e.g., by an eccentric carried by the pump crank shaft.
  • the pump piston is similarly driven by an eccentric, the pump and inlet valve eccentrics being angularly displaced in their respective positions at the crank shaft, as to delay opening of the inlet valve for a predetermined period following a pump stroke, in order to enable decompression of the liquid in the pump chamber.
  • the average rotational velocity of the stepping motor is controlled throughout each full crank shaft rotation, so as to enable a precisely selected cycle of pump operation.
  • the speed of the motor is so regulated in conjunction with the mechanical actuation of the pump piston and inlet valve as to provide (at the low flow rates where such behavior is critical) a very short duration fill period--which implies a rapid withdrawal of the piston or plunger from the pump cylinder.
  • the second portion of the pumping cycle which corresponds to pumping or displacing the liquid from the pump toward the chromatographic column, is effected under crank shaft rotation (as a function of time) such that the axial displacement of the piston is relatively linear as a function of time.
  • Fig. 6(A) shows compensation for pulsations in the case where a fluid is delivered under high pressure
  • Fig. 6(B) shows pulsation compensation in the case where the delivery of a fluid is effected under low pressure
  • the reference symbol a represents a pulsing flow in the case where the speed of rotation of the cam is kept constant
  • b represents the speed of rotation of the cam controlled so as to compensate the pulsing flow
  • c represents the pulsing flow thus compensated.
  • US-A-4 359 312 discloses a reciprocating type fluid delivery pump of the type mentioned at the beginning, however with two piston pumps instead of plunger pumps.
  • the cam means is designed such that
  • a primary object of the present invention to provide a reciprocating type fluid delivery pump which is so designed that it is possible to more favorably compensate for pulsations occurring due to the compressibility of a fluid and other factors during the delivery starting period in a state wherein no load is applied to the driving motor.
  • the present invention provides a reciprocating type fluid delivery pump of the type mentioned at the beginning, which is characterized in that
  • Fig. 2 shows a small-volume plunger reciprocating type fluid delivery pump to which the present invention is applied.
  • the reference numeral 10 denotes a driving stepping motor, and 11 a cam shaft.
  • the rotation of the stepping motor 10 is transmitted to the cam shaft 11 through a small pulley 12, a belt 13 and a large pulley 14 which is secured to the cam shaft 11.
  • the cam shaft 11 has two cams 15 and 16 secured thereto for driving two pump heads, respectively.
  • the cam shaft 11 further has a disk 17 secured thereto.
  • the disk 17 is provided with a bore 18, so that the home position relative to the rotational angle of the cams 15 and 16 is detected by detecting the bore 18 by means of a photocoupler 19.
  • a crosshead 20 The proximal end of a crosshead 20 is in contact with the cam 15 so that the crosshead 20 performs a reciprocating motion.
  • a plunger 21 of a first pump head 24 is secured to the other end of the crosshead 20.
  • the proximal end of a crosshead 22 is in contact with the other cam 16 so that the crosshead 22 performs a reciprocating motion, and a plunger 23 of a second pump head 25 is secured to the crosshead 22.
  • Cams 15 and 16 which will be described later in detail, are designed to have configurations that provide angle-plunger speed characteristics as shown in Fig. 1.
  • the reciprocating motion of the plunger 21 causes a fluid 26 to be delivered to a flow path leading to a pressure sensor 28 from a suction filter 29 and an inlet block 27.
  • the reciprocating motion of the plunger 23 causes the fluid 26 to be delivered to a flow path leading to the pressure sensor 28 from the suction filter 29 and the inlet block 27.
  • the reference symbol a denotes an inlet check valve, b an outlet check valve, and c seal member.
  • the fluids respectively delivered from the first and second pump heads 24 and 25 are joined together and are then delivered from a pump outlet 30 to a flow path which leads to a column.
  • Reference numeral 31 denotes a drain flow path, and 32 a drain bin.
  • the reference numeral 33 denotes a CPU.
  • a pressure signal from the pressure sensor 28 and a home position detecting signal from the photocoupler 19 are sent to CPU 33.
  • CPU 33 controls the speed of rotation of the stepping motor 10.
  • the configurations of the cams 15 and 16 are determined so that the dr/d ⁇ (the plunger speed at the time of uniform rotation) characteristics with respect to the cam rotational angle ⁇ are set such as those shown in Fig. 1.
  • the curves 1a and 2a represent the dr/d ⁇ characteristics of the first and second pump heads, respectively.
  • Figs. 3(A)-3(C) show the relationship between the pressure and the rotational speed of the driving motor in this embodiment.
  • Fig. 3(A) shows the pulsation compensation that is made in the case where fluid delivery is carried out under substantially no pressure. If the driving motor is rotated at constant velocity, excesses A occur in the delivery flow rate during the delivery starting period in each cycle, as shown by graph a. Therefore, the driving motor is decelerated such that the rotational speed of each cam is reduced during each delivery starting period, as shown by graph b. As a result, the delivery flow rate becomes constant as shown by graph c.
  • Fig. 3(B) shows the pulsation compensation that is made in the case where the fluid delivery is carried out under low pressure. If the driving motor is rotated at constant velocity, an excess A′ in the delivery flow rate appears in the temporally latter portion of each excess delivery period, as shown by graph a. Therefore, the rotational speed of the motor is reduced as shown by graph b. As a result, the delivery flow rate becomes constant as shown by graph c.
  • Fig. 3(C) shows the pulsation compensation made in the case where the fluid delivery is carried out under high pressure.
  • deficiencies in the delivery flow rate due to high pressure and excesses in the delivery flow rate due to high pressure and excesses in the delivery flow rate due to the modification of the cams cancel each other, so that the delivery flow rate in graph a at the time when the driving motor is rotated at constant velocity is constant. Accordingly, there is no need to compensate the rotational speed in graph b of the driving motor.
  • the relationship between the pressure and the optimal amount of compensation i.e., the driving motor deceleration period
  • the relationship between the pressure and the optimal amount of compensation depends on the kind of fluid delivered, it may be possible to set the relationship in advance or obtain it automatically while monitoring the level of the pressure.
  • the compensation that is made by decelerating the driving motor is conducted in a relatively low flow rate region where it is highly essential to reduce pulsations.
  • flow rate regions where the flow rate is high and fluid delivery is effected at high frequency pulsations are small, so that it is unnecessary to reduce the rotational speed of the driving motor to compensate.
  • the cams may be rotated at constant velocity.
  • the configurations of cams for reciprocating respective plungers are improved so that, when the driving motor is rotated at constant velocity, the delivery flow rate during the delivery starting period of each of the plungers is in excess of that during the other periods of the cycle. Therefore, the speed of rotation of the driving motor is controlled in such a manner that, when the fluid is delivered under low pressure, the rotational speed is reduced, whereas, when the fluid delivery is carried out under high pressure, the motor is rotated at constant velocity. Accordingly, the load on the driving motor is reduced and it is possible to employ a driving motor having a relatively low output in comparison with the conventional compensation wherein the rotational speed of the driving motor is increased under high pressure.

Claims (3)

  1. Fluidabgabepumpe vom hin- und hergehenden Typ mit zwei Pumpenköpfen (24, 25), umfassend:
    einen Antriebsmotor (10);
    ein Paar Plunger (21, 23) zum Antreiben der beiden Pumpenköpfe (24, 25), jeweils;
    eine Umwandlungseinrichtung (11, 13 - 16, 20, 22) zum Umwandeln der Drehbewegung des Antriebsmotors (10) in hin- und hergehende Bewegung von jedem Plunger (21, 23), wobei die Umwandlungseinrichtung (11, 13 - 16, 20, 22) eine mit den Plungern (21, 23) in Eingriff bringbare Nocken- bzw. Nockenscheibeneinrichtung (15, 16) zum Hin- und Herbewegen der Plunger (21, 23) aufweist, und worin die Nocken-bzw. Nockenscheibeneinrichtung (15, 16) eine derartige Konfiguration hat, daß dann, wenn der Antriebsmotor (10) mit konstanter Geschwindigkeit gedreht wird, die Abgabeströmungsrate während der Abgabebeginnperiode von jedem der Plunger (21, 23) im Übermaß gegenüber derjenigen während der anderen Perioden des Zyklus' ist; und
    eine Einrichtung (33) zum wahlweisen Verzögern des Antriebsmotors (10) während der Übermaßabgabeperiode, wenn die Fluidabgabe nicht unter hohem Druck ausgeführt wird;
    worin die Nocken- bzw. Nockenscheibeneinrichtung (15, 16) derart ausgebildet ist, daß die Abgabegeschwindigkeit von jedem Plunger (21, 23) einen ersten Anstieg hat, während die Abgabegeschwindigkeit des anderen Plungers (23, 21) noch konstant ist, und einen zweiten Anstieg, während die Abgabegeschwindigkeit des anderen Plungers (21, 23) abnimmt;
    dadurch gekennzeichnet, daß
    (a) der erste Anstieg ein relativ steiler Anstieg ist; und
    (b) die Abgabegeschwindigkeit von jedem Plunger (21, 23) ein kurzes Plateau hat, während die Abgabegeschwindigkeit des anderen Plungers (23, 21) noch konstant ist, wobei das Plateau den ersten Anstieg mit dem zweiten Anstieg verbindet.
  2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Nocken- bzw. Nockenscheibeneinrichtung (15, 16) ein Paar Nocken bzw. Nockenscheiben aufweist, wobei jede Nocke bzw. Nockenscheibe mit einem entsprechenden einen der Plunger (21, 23) in Eingriff tritt.
  3. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Verzögerungseinrichtung (33) den Antriebsmotor (10) während der Übermaßabgabeperiode, wenn die Fluidabgabe unter niedrigem Druck ausgeführt wird, verzögert.
EP88116666A 1988-03-28 1988-10-07 Flüssigkeitsfördernde Kolbenpumpe Expired - Lifetime EP0334994B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP77585/88 1988-03-28
JP63077585A JP2745526B2 (ja) 1988-03-28 1988-03-28 往復動型送液ポンプ

Publications (2)

Publication Number Publication Date
EP0334994A1 EP0334994A1 (de) 1989-10-04
EP0334994B1 true EP0334994B1 (de) 1992-09-23

Family

ID=13638054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88116666A Expired - Lifetime EP0334994B1 (de) 1988-03-28 1988-10-07 Flüssigkeitsfördernde Kolbenpumpe

Country Status (4)

Country Link
US (1) US5114314A (de)
EP (1) EP0334994B1 (de)
JP (1) JP2745526B2 (de)
DE (1) DE3874883T2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100523496C (zh) * 2003-12-20 2009-08-05 Itw有限公司 泵
DE102012105323A1 (de) 2012-06-19 2013-12-19 Dionex Softron Gmbh Steuervorrichtung zur Steuerung einer Kolbenpumpeneinheit für die Flüssigkeitschromatographie, insbesondere die Hochleistungsflüssigkeitschromatographie
US10801479B2 (en) 2011-08-19 2020-10-13 Dionex Softon Gmbh Device for controlling a piston pump unit for liquid chromatography

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GB9526653D0 (en) * 1995-12-29 1996-02-28 Shine Thomas A Fluid delivery device
SE9600748D0 (sv) * 1996-02-27 1996-02-27 Pharmacia Biotech Ab Pump
EP0801982B1 (de) * 1996-04-18 2002-08-28 Walu Labortechnik GmbH Kolbenbürette
US5971714A (en) * 1996-05-29 1999-10-26 Graco Inc Electronic CAM compensation of pressure change of servo controlled pumps
JPH106954A (ja) * 1996-06-27 1998-01-13 Unisia Jecs Corp ポンプ装置およびブレーキ制御装置
JPH10176654A (ja) * 1996-12-16 1998-06-30 Unisia Jecs Corp ポンプ装置
JPH11218082A (ja) * 1998-02-02 1999-08-10 Ouken Seiko Kk 減圧ポンプ
JP3670851B2 (ja) * 1998-07-21 2005-07-13 アクト・サイエンス株式会社 液体クロマトグラフィー用送液ポンプ
JP3995227B2 (ja) * 1999-01-21 2007-10-24 株式会社スギノマシン 液体加圧装置
FR2817594B1 (fr) * 2000-12-04 2005-07-01 Exel Ind Dispositif de pompage pour produits epais ou sensibles a la turbulence
WO2002103202A1 (fr) * 2001-06-16 2002-12-27 Musashi Engineering, Inc. Dispositif servant a delivrer une quantite fixe de liquide
JP4626270B2 (ja) * 2004-11-01 2011-02-02 株式会社島津製作所 送液装置
US8241013B2 (en) * 2005-10-27 2012-08-14 Waters Technologies Corporation Serial capillary pump
WO2008039787A2 (en) * 2006-09-26 2008-04-03 Graco Minnesota Inc. Electronic camshaft motor control for piston pump
WO2009081399A1 (en) * 2007-12-21 2009-07-02 Medingo Ltd. Devices and methods for powering a medical device
ES2336177B1 (es) * 2008-01-08 2011-02-03 Manuel Torres Martinez Bomba con recuperador de empuje directo para la impulsion de fluidos.
US8235689B2 (en) * 2008-11-03 2012-08-07 Gojo Industries, Inc. Piston pump with rotating pump actuator
US9618486B2 (en) * 2012-03-07 2017-04-11 Waters Technologies Corporation Limiting a rate of pressurization in a pressurized flow system having a configurable system volume
US9107986B2 (en) * 2013-03-11 2015-08-18 Boston Scientific Limited Double action infusion pump
CN103195681B (zh) * 2013-04-12 2015-06-24 中国人民解放军军事医学科学院卫生装备研究所 一种医用水刀的双凸轮传动机构
US9714650B2 (en) 2013-06-11 2017-07-25 Matthew G. Morris, Jr. Pumping system
FR3044052B1 (fr) * 2015-11-25 2019-09-13 Exel Industries Pompe d'alimentation d'un systeme d'application d'un produit de revetement liquide

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Cited By (6)

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Publication number Priority date Publication date Assignee Title
CN100523496C (zh) * 2003-12-20 2009-08-05 Itw有限公司 泵
US10801479B2 (en) 2011-08-19 2020-10-13 Dionex Softon Gmbh Device for controlling a piston pump unit for liquid chromatography
US11959467B2 (en) 2011-08-19 2024-04-16 Dionex Softron Gmbh Device for controlling a piston pump unit for liquid chromatography
DE102012105323A1 (de) 2012-06-19 2013-12-19 Dionex Softron Gmbh Steuervorrichtung zur Steuerung einer Kolbenpumpeneinheit für die Flüssigkeitschromatographie, insbesondere die Hochleistungsflüssigkeitschromatographie
DE102012105323B4 (de) * 2012-06-19 2017-03-16 Dionex Softron Gmbh Steuervorrichtung zur Steuerung einer Kolbenpumpeneinheit für die Flüssigkeitschromatographie, insbesondere die Hochleistungsflüssigkeitschromatographie
US9624923B2 (en) 2012-06-19 2017-04-18 Dionex Softron Gmbh Control arrangement for controlling a piston pump unit for liquid chromatography

Also Published As

Publication number Publication date
JP2745526B2 (ja) 1998-04-28
JPH01247769A (ja) 1989-10-03
EP0334994A1 (de) 1989-10-04
DE3874883T2 (de) 1993-03-04
DE3874883D1 (de) 1992-10-29
US5114314A (en) 1992-05-19

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